US8038119B2 - Metering device - Google Patents

Metering device Download PDF

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Publication number
US8038119B2
US8038119B2 US10/595,159 US59515904A US8038119B2 US 8038119 B2 US8038119 B2 US 8038119B2 US 59515904 A US59515904 A US 59515904A US 8038119 B2 US8038119 B2 US 8038119B2
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Prior art keywords
end cap
metering device
actuator
housing
stop
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US10/595,159
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US20070131884A1 (en
Inventor
Georg Bachmaier
Bernhard Fischer
Bernhard Gottlieb
Andreas Kappel
Tim Schwebel
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Vitesco Technologies GmbH
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Siemens AG
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GOTTLIEB, BERNHARD, DR., KAPPEL, ANDREAS, DR., SCHWEBEL, TIM, DR., BACHMAIER, GEORG, FISCHER, BERNHARD
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Publication of US8038119B2 publication Critical patent/US8038119B2/en
Assigned to CONTINENTAL AUTOMOTIVE GMBH reassignment CONTINENTAL AUTOMOTIVE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SIEMENS AKTIENGESELLSCHAFT
Assigned to Vitesco Technologies GmbH reassignment Vitesco Technologies GmbH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CONTINENTAL AUTOMOTIVE GMBH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting

Definitions

  • the invention relates to a metering device, especially with an actuator unit as a drive for a valve in a common-rail diesel injector.
  • the elongation ratio of the piezoactuator which can be achieved by the inverse piezoelectric effect in high-performance ceramics as a result of the application of a maximum field strength of appr. 2 KV/mm permissible for continuous operation only amounts to 1.2-1.4 promille (that is 1.2-1.4 pm elongation per 1 mm length of the piezoactuator).
  • the inverse piezoelectric effect produces an elongation of maximum 56 ⁇ m.
  • the piezoactuator is a component with a domain structure and hysteresis the temperature expansion coefficient is heavily dependent on the polarization state and the previous history of mechanical and electrical stress on the piezoactuator.
  • the dependency of the length of the piezoactuator on temperature is non-linear.
  • the coefficient of thermal expansion can assume values for the same piezoactuator ranging from ⁇ 5*10 ⁇ 6 1/K up to +7*10 ⁇ 6 1/K [1].
  • the positive change in length caused by the electrical charging of the piezoactuator is used in current common rail diesel injectors to close a sealing element.
  • a “thermal gap”, that is a safety margin of typically 3-5 pm between the freely-moveable end of a piezoelectric actuator unit (PAU) which is embodied as a plunger or which is rigidly mechanically coupled to a plunger and the sealing element is provided.
  • the PAU consists of an upper end cap which is mechanically rigidly supported and which contains at least one whole through which the electric connections of the piezoactuator can be routed outwards, a lower end cap which is embodied as a plunger or which is mechanically rigidly coupled to a plunger, the piezoactuator and a tubular spring into which the piezoactuator is welded under a pre-tensioning pressure of appr. 600N-800N between the two end caps. It is not possible to ideally strike a thermal balance between the actuator housing and the PAU. The safety margin is used, in the event of a greater thermal expansion of the PAU relative to the actuator housing, so that the sealing element is opened and there is continuous leakage through the servo valve as a result. However the fluctuations in the PMA temperature coefficients make it clear that even such a margin is not always sufficient.
  • the fluid pressure which is exerted on the sealing element from the other direction can however subsequently in the switched-on state of the injector reach a pressure of up to 2000 bar and give rise to forces or opposing forces of up to 600 N. During injector operation these forces ensure a defined closure of the sealing element despite an overextension of the actuator.
  • An internal high-pressure pump in the motor vehicle when another attempt is made to start the engine, and thereby the injector, is however no longer in a position if the injector is still hot, to build up the necessary pressure in order to close the sealing element so that this leads to malfunctions of the injector.
  • FIG. 1 An actuator unit A in accordance with the prior art is shown in FIG. 1 . It consists of a housing 1 , a piezoactuator 2 with a tubular spring 8 , a first and a second end cap 3 , 7 , with the first end cap 3 being provided with a plunger 4 .
  • the piezoactuator 2 is welded into the tubular spring 8 under a pre-tensioning pressure of appr. 600 to 800 N in order to avoid damaging tensile stresses during operation.
  • a membrane 5 typically made of metal, enables a seal to be provided between the piezoactuator and fuel.
  • the second end cap 7 is supported against the housing 1 whereas the first end cap 3 on activation presses together with the plunger 4 against the sealing element 6 of the seating valve 12 .
  • the sealing element 6 implemented as a ball, is held in the seat 12 with the aid of a weak return spring (not shown) at the pressure of approximately 5N.
  • a weak return spring not shown
  • thermal changes are not short term processes in the range of below 10 ms but take seconds or minutes to occur.
  • This type of slow expansion of the actuator 2 can however be balanced out by a hydraulic compensation element X, as shown in FIG. 1 a .
  • a hydraulic compensation element X is preferably seated between the end cap 7 of the actuator 2 and the other end of the housing 1 and is attached to the housing.
  • the thermal expansion of the actuator now occurs in the direction of the end cap 7 and does not absolutely lead to a change in the distance between the sealing element 6 and the plunger 4 and thus also does not lead to permanent leakages.
  • the hydraulic compensation element X however exhibits a stiffness comparable with a rigid body when force is applied to it for short periods, in which case despite this stiffness the hydraulic compensation element or a component of the hydraulic compensation element which is connected indirectly or directly to the piezoactuator gives way by a negligible amount.
  • these distances which are in themselves negligible, add up with multiple activation of the piezoactuator so that the hydraulic compensation aliment or the component of the hydraulic compensation element is shifted upwards by the maximum deflection of the piezoactuator and thereby the gap between the piston 4 and the sealing element 6 is enlarged such that the piston no longer reaches this sealing element on repeated actuation of the piezoactuator. Opening the sealing element 6 is no longer possible in this case.
  • the object of the invention is thus to specify a device and/or a method by which a predetermined distance between a sealing element and an actuator unit can be constantly maintained.
  • a metering device comprising:
  • This metering device provides the advantage that even with fluctuating operating temperatures a smallest possible distance between the sealing element and the actuator is maintained. This always guarantees an opening of the sealing element by the actuator, with the compensation for the temperature expansion of the actuator able to be achieved by the hydraulic compensation element being able to be maintained.
  • the first end cap is moved past the stop and using a subsequent second rotation of the end cap and the stop they are opposite each other so that, with a movement of the end cap in the direction of the hydraulic compensation element the end cap hits the stop and this movement is blocked.
  • the method corresponds to a simple key-lock relationship between the end cap and the stop. It is especially suitable and safe for simple manufacturing of the metering device.
  • the key-lock relationship preferably represents a bayonet lock.
  • the actuator is preferably a piezoactuator.
  • FIG. 1 shows a conventional metering device
  • FIG. 1A a metering device with a stop arrangement and a hydraulic compensation element
  • FIG. 3 examples of the geometry of an end cap
  • FIG. 4 the end cap guided through a housing and depicted in FIG. 3 .
  • FIG. 5 a three-dimensional view of the end cap guided through the housing.
  • the hydraulic compensation element 13 can be installed in the metering device in a simple manner between an end of the housing 1 and the piezoactuator 2 , a process which advantageously simplifies the integration into or modification of existing injectors.
  • the hydraulic compensation element is preferably fixed to the inner wall of the housing 1 .
  • the hydraulic compensation element 13 is basically rigid in relation to the brief application of a force and simultaneously gives way to a thermally-induced change in length of the actuator.
  • the hydraulic compensation element 13 preferably features at least one hydraulic chamber 13 c , a hollow-cylinder-shaped housing 13 a and a piston 13 b , with the piston 13 b or the housing 13 a being connected to the second end cap 7 ′ of the actuator 2 .
  • the hydraulic chamber 13 c lies between axially effective pressure surfaces of the piston and the housing in each case and between at least two clearances 13 g , which are embodied between the piston and the housing.
  • the axially effective pressure surfaces are essentially aligned axially.
  • the term “axial” is understood as being the direction of the force effects and transmissions of the piezoactuator or of the hydraulic compensation element. “Axial” is however also taken to mean “essentially axial”.
  • the clearances 13 g basically have a strongly fluid-restricting effect.
  • the hydraulic compensation element can be filled under pressure with a fluid, preferably silicon oil. It his preferred that the hydraulic compensation element features an axial through-hole 13 d through which the leads 17 to the piezoactuator 2 can be routed. In particular the piston 13 b is provided with this through-hole 13 d.
  • the piston 13 b and the housing 13 a with a slow thermally induced length change of the actuator are able to be displaced relative to each other without any force being exerted so that the hydraulic compensation element gives way during this time.
  • the piston With a brief application of a force the piston only moves by a negligible amount relative to the housing however so that the hydraulic compensation element can be considered as being rigid.
  • the hydraulic compensation element for increased rigidity features several, especially two, hydraulic chambers.
  • the housing 13 a a is expanded by a part to form a further hydraulic chamber similar to the first hydraulic chamber 13 c between the piston 13 b and the housing 13 a as previously stated.
  • the hydraulic compensation element would operate bidirectionally in this case.
  • the hydraulic compensation element 13 is provided with membranes 13 f on its two end faces which preferably are attached to the piston 13 b and the housing 13 a .
  • the membranes storage volumes 13 e are embodied between the housing, the membranes and the piston.
  • the membranes can also expand at increased temperature so that they can compensate for a thermal volume change of the fluid in the hydraulic compensation element. They each preferably have coefficients of thermal expansion which differ from those of the housing and/or the piston.
  • the membranes of preferably embodied as annular flat membranes.
  • the hydraulic compensation element is hydraulically connected via a hole in the housing 13 a of the hydraulic compensation element with a compensation store in order to compensate for an increasing volume change of the fluid located in the hydraulic compensation element at increased temperature even better than with the previously mentioned membranes 13 f and storage volumes 13 e .
  • the compensation store preferably features a membrane which can be implemented as an elastic sleeve and a storage volume enclosed below it.
  • the elastic sleeve of the compensation store is preferably arranged on the lateral surface of the housing 13 a . At increased temperature of the fluid the membrane expands so that the fluid in the hydraulic compensation area has a greater volume at its disposal and thus no disruptive net force effect between the piston and the housing arises.
  • the housing 13 a of a hydraulic compensation element is mechanically connected by means of a spacer to the inner wall of the housing 1 of the metering device.
  • the compensation store can however also be implemented in the form of an external hydrostore.
  • the piston 13 b or the housing 13 a are also preferably provided with axial holes, which connect the storage volume 13 e to the hydraulic chambers 13 c , in order to facilitate the fluid flowback during the blanking interval of the piezoactuator into the hydraulic chambers and into the storage volume.
  • the openings of the holes are provided in such cases with non-return valves known as flapper valves, so that the opening of the holes close during a brief deflection of the piezoactuator and thereby the hydraulic compensation element remains rigid when a force is briefly applied to it.
  • flapper valves open in these cases as a result of a pressure drop in the hydraulic chambers 13 c.
  • the piston and the housing consist of the same material or materials with the same coefficients of thermal expansion. To avoid sticking a sufficiently large gap between a piston and cylinder in a range of 10 to 50 ⁇ m combined with a fluid of higher basic viscosity in the range of 100 to 1000 Centistokes with a sufficient guide length of the piston in the housing to avoid tilting is to be selected.
  • a material is then selected for the piston 3 with a lower thermal expansion which means that the piston does not begin to stick in narrow clearances 13 g.
  • the temperature influence on the gap flow between the clearances 13 g in the state of the hydraulic system when subjected to a load by the actuator can be compensated for in wide ranges if the piston has a suitably selected higher thermal expansion than the housing.
  • the explanation is to be found in the fact that the viscosity of the hydraulic fluid reduces in accordance with an exponentially with temperature and the volume flow of the hydraulic fluids along the clearances increases exponentially accordingly.
  • the volume flow in this case is proportional to the third power of the width of the clearances which can also be referred to as the size of fit.
  • the size of fit increases linearly with temperature and thus the temperature effects on the size of fit and on the viscosity are opposing.
  • the housing 1 of the metering device is lengthened when necessary in comparison to the original layout shown in FIG. 1 to enable the hydraulic compensation element 13 to be accommodated.
  • the second end cap 7 ′ is welded to the piston 13 b of the hydraulic compensation element.
  • the housing 1 is sealed in the upwards direction by a closure element 15 , preferably a fixed support.
  • the piezoelectric actuator unit PAU mentioned at the start of the description comprises the arrangement of features which are mechanically indirectly or directly connected to the piezoactuator and features, in addition to the known features from FIG. 1 a first, lower and modified end cap 3 ′ which is a equipped with a plunger B pointing towards the valve unit B.
  • the valve unit B is taken to mean at least an arrangement which comprises the valve seat 12 and the sealing element 6 .
  • the valve unit can additionally have inlets and returns 9 , 10 for the fuel.
  • the end cap 3 ′ is preferably frustoconical, with its lateral surface being stepped.
  • end cap 3 ′ should however feature at least two ears 3 ′ a , of which the surfaces aligned essentially axially, in the opposite direction to the sealing element 6 , on withdrawal of the actuator, come up against surfaces 14 a of the stop 14 which are also aligned axially.
  • a membrane 5 seals piezoactuator 2 against fuel in the metering device, which on opening of the sealing element 6 flows from the inlet 9 through the seat valve 12 to the return 10 .
  • the membrane 5 preferably connects the housing 1 to the end cap 3 ′.
  • the piezoactuator 2 is preferably also provided with a second upper end cap 7 ′ which is connected to the hydraulic compensation element. It is preferred that the end cap 7 ′ has an axial hole 16 for connecting leads 17 , to simplify the contacting of the piezoactuator 2 to control electronics (not shown).
  • a significant element of the metering device is the stop 14 , which counteracts a change in the position of equilibrium of the piston 13 b of the hydraulic compensation element, and thus also the position of the end cap 3 ′.
  • the stop 14 can be seen as a tapering in the internal diameter of the housing 1 .
  • the term “internal diameter” or “diameter” is always taken to mean a trans-axial diameter which runs at right angles to the longitudinal axis of the actuator.
  • the stop is preferably penetrated by two holes. The stop allows the actuator to expand in the direction of the sealing element 6 , but prevents the end cap 3 ′ from withdrawing beyond a predefined distance from the sealing element 6 .
  • a fine adjustment of the maximum gap between the plunger 4 of the end cap 3 ′ and the valve seat 12 can be obtained with the aid of shims.
  • the requirements for the accuracy of this fine adjustment however are very small as a result of the compensating effect of the hydraulic compensation elements.
  • the stop 14 can be embodied in a plurality of variants. Of significance for an actual embodiment is its installation below the piezoactuator, to allow the expansion of the actuator upwards or in the opposite direction towards the sealing element.
  • FIG. 3 shows the lower end cap 3 ′ as a frustoconical form with a lateral surface which is provided with steps.
  • the end cap in particular features two ears 3 ′ a on the trans-axial surface of which an outer diameter of the end cap is present which is larger than the minimum internal diameter of the stop or of the taper 14 of the housing 1 .
  • the ears 3 ′ a of the end cap 3 ′ are especially moved past the cutouts 14 a of the stop 14 . Subsequently the end cap is rotated so there a pulling back of the end cap means that the ears 3 ′ a can no longer be moved past the stop.
  • FIG. 4 shows how the end cap 3 ′ a lies opposite the stop at 14 before the metering device is in its completely assembled state.
  • the cross sectional view on the left shows how the external dimension of the end cap 3 ′ at the level of the ears 3 ′ a is greater than the minimum internal diameter of the stop.
  • the cutouts in the stop are shown by the number 14 a .
  • the arrangement of the cutout 14 a and the stop in relation to each other can clearly be seen.
  • the position of the ears 3 ′ a of the end cap in this view is such that the end cap 3 ′ without being rotated can be moved past the stop in a straight line, in that the ears 3 ′ a can be passed through the cutouts 14 a .
  • the end cap 3 ′ is also basically the matching part for the stop 14 so that a key-lock arrangement is basically formed by the two parts.
  • the stop and the end cap thus form a bayonet locking connection.
  • FIG. 5 shows a further three-dimensional view of the lower area of the metering device before it is in its assembled state. As shown in FIG. 4 the ears 3 ′ a lie opposite the cutouts 14 a , so that the end cap 3 ′ can be moved past the stop 14 .
  • a further option for embodiment of a stop 14 consists of a direct connection between the plunger 4 and the sealing element 6 of the seat valve 12 , so that the plunger also takes over the role of the sealing element.
  • the end cap is withdrawn the valve seat itself then hits the stop element, since the sealing element or the plunger has a diameter so that it cannot move past the valve seat.
  • the stop 14 can also be replaced by an additional spring between piston 13 b and the fixed support 15 .
  • the pre-tensioning of the spring in the manufacturing of the metering device ensures an effective downwards force which operates via the plunger 4 on the sealing element 6 of the valve unit B and operates against a change in the equilibrium position of the piston. This means that the piston is always subject to a reset force, to prevent a shift in the equilibrium position of the piston and guarantee a defined contact between the plunger and the sealing element.
  • the elasticity of the membrane 5 is also suitable as a reset element for a desired equilibrium position. Welding of the membrane 5 onto the end cap 3 ′ and onto the housing 1 ensures in this case that the end cap is prevented from turning in the position in which the cutouts 14 a and the ears 3 ′ a are opposite each other in the assembled state of the metering device, and the end cap is thereby accidentally pulled past the stop again.
  • the inventive metering device is used in a common-rail diesel injector.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)
US10/595,159 2003-09-12 2004-09-10 Metering device Active 2027-12-05 US8038119B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10342308.7 2003-09-12
DE10342308 2003-09-12
DE10342308 2003-09-12
PCT/EP2004/052130 WO2005026532A1 (de) 2003-09-12 2004-09-10 Dosiervorrichtung

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US20070131884A1 US20070131884A1 (en) 2007-06-14
US8038119B2 true US8038119B2 (en) 2011-10-18

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Application Number Title Priority Date Filing Date
US10/595,159 Active 2027-12-05 US8038119B2 (en) 2003-09-12 2004-09-10 Metering device

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US (1) US8038119B2 (de)
EP (1) EP1664525B1 (de)
JP (1) JP4264449B2 (de)
DE (1) DE502004006944D1 (de)
WO (1) WO2005026532A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10900587B2 (en) 2018-03-29 2021-01-26 Hamilton Sunstrand Corporation Valves

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005024049A1 (de) * 2005-05-25 2006-11-30 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung
US20070007363A1 (en) * 2005-07-04 2007-01-11 Hitachi, Ltd. Fuel injection valve
GB201512350D0 (en) * 2015-07-15 2015-08-19 Delphi Int Operations Lux Srl Servo actuator for fuel injector
EP3139028A1 (de) * 2015-09-03 2017-03-08 Delphi International Operations Luxembourg S.à r.l. Zweiseitig gesockelte koppler für stellantrieb

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2922614A (en) * 1956-06-18 1960-01-26 Honeywell Regulator Co Hum-free solenoid device
US3418980A (en) * 1965-09-01 1968-12-31 Physics Internat Company Fuel injector-ignitor system for internal combustion engines
JPS618462A (ja) 1984-06-25 1986-01-16 Nippon Soken Inc 電歪式燃料噴射弁
US4725002A (en) * 1985-09-17 1988-02-16 Robert Bosch Gmbh Measuring valve for dosing liquids or gases
EP0324905A1 (de) 1988-01-21 1989-07-26 Toyota Jidosha Kabushiki Kaisha Kraftstoffeinspritzventil für einen Motor
EP0869278A1 (de) 1997-04-04 1998-10-07 Siemens Aktiengesellschaft Einspritzventil mit Mitteln zur Kompensation der thermischen Längenänderung eines Piezoaktors
DE19826341A1 (de) 1998-06-12 1999-12-16 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19929589A1 (de) 1998-07-02 2000-01-13 Avl List Gmbh Einspritzeinrichtung für eine Brennkraftmaschine
DE19950762A1 (de) 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
US20020139863A1 (en) 2000-10-11 2002-10-03 Jack Lorraine Compensator assembly having a flexible diaphragm and an internal filling tube for a fuel injector and method
US20030042325A1 (en) 2001-08-31 2003-03-06 Siemens Automotive Corporation Twin tube hydraulic compesator for a fuel injector
US20030098428A1 (en) 2000-04-20 2003-05-29 Patrick Mattes Valve for controlling the flow fluids
DE10162250A1 (de) 2001-12-18 2003-07-03 Bosch Gmbh Robert Brennstoffeinspritzventil
US20030150939A1 (en) 2002-02-11 2003-08-14 Siemens Vdo Automotive Corporation Method of filling and degassifying fluid in a hydraulic compensator for a fuel injector

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2922614A (en) * 1956-06-18 1960-01-26 Honeywell Regulator Co Hum-free solenoid device
US3418980A (en) * 1965-09-01 1968-12-31 Physics Internat Company Fuel injector-ignitor system for internal combustion engines
JPS618462A (ja) 1984-06-25 1986-01-16 Nippon Soken Inc 電歪式燃料噴射弁
US4725002A (en) * 1985-09-17 1988-02-16 Robert Bosch Gmbh Measuring valve for dosing liquids or gases
EP0324905A1 (de) 1988-01-21 1989-07-26 Toyota Jidosha Kabushiki Kaisha Kraftstoffeinspritzventil für einen Motor
EP0869278A1 (de) 1997-04-04 1998-10-07 Siemens Aktiengesellschaft Einspritzventil mit Mitteln zur Kompensation der thermischen Längenänderung eines Piezoaktors
DE19826341A1 (de) 1998-06-12 1999-12-16 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19929589A1 (de) 1998-07-02 2000-01-13 Avl List Gmbh Einspritzeinrichtung für eine Brennkraftmaschine
DE19950762A1 (de) 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
US20030098428A1 (en) 2000-04-20 2003-05-29 Patrick Mattes Valve for controlling the flow fluids
US20020139863A1 (en) 2000-10-11 2002-10-03 Jack Lorraine Compensator assembly having a flexible diaphragm and an internal filling tube for a fuel injector and method
US20030042325A1 (en) 2001-08-31 2003-03-06 Siemens Automotive Corporation Twin tube hydraulic compesator for a fuel injector
DE10162250A1 (de) 2001-12-18 2003-07-03 Bosch Gmbh Robert Brennstoffeinspritzventil
US6953158B2 (en) 2001-12-18 2005-10-11 Robert Bosch Gmbh Fuel injection valve
US20030150939A1 (en) 2002-02-11 2003-08-14 Siemens Vdo Automotive Corporation Method of filling and degassifying fluid in a hydraulic compensator for a fuel injector

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
Notification of International Search Report, International Search Report in German & English Translation of Search Report; PCT/EP2004/052130; 14 Pgs, Dec. 2004.
PCT International Search Report PCT/EP2004/052130, 2 pages, Dec. 14, 2004.
Written Opinion in German from PCT/EP2004/052130; 5 Pgs, Dec. 2004.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10900587B2 (en) 2018-03-29 2021-01-26 Hamilton Sunstrand Corporation Valves

Also Published As

Publication number Publication date
JP2007505254A (ja) 2007-03-08
US20070131884A1 (en) 2007-06-14
EP1664525A1 (de) 2006-06-07
JP4264449B2 (ja) 2009-05-20
WO2005026532A1 (de) 2005-03-24
DE502004006944D1 (de) 2008-06-05
EP1664525B1 (de) 2008-04-23

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